JP2005325840A - Pump having reciprocating movement vane and non-circular cross section rotor - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide an inexpensive rotary vane pump usable for fluid having a wide range of viscosity and having a comparatively simple structure. <P>SOLUTION: This rotary vane pump 10 comprises a stationary housing 12 having an inlet 30, an outlet 32, and a pump chamber 14 having a bore 34 having at least a part of circular cross section which are sequentially communicated through fluid, a rotor 20 attached rotatably in a circular cross section part 34 of a bore 14 and having cam surfaces 60, 62, 64 having non-circular central rotary axial line and cross section, and a vane 22 attached in the housing 12 to reciprocate and move between a protrusion position and a retraction position for the housing 12, having a contact face 80 sealing and coming into contact with the cam surfaces 60, 62, 64 of the rotor 20, and reciprocated by rotation of the rotor to maintain separation of fluid by the vane 22 and the rotor 20 between the inlet 30 and the outlet 32. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

  The present invention relates to an impeller pump, i.e., a housing having an internal rotor (the "stator" portion of the pump), and a rotor chamber disposed between the rotor and the rotor chamber wall to separate the rotor chamber into an introduction region and a discharge region or a discharge region. The present invention relates to a rotary vane pump of a movable vane type. The rotation of the rotor performs the action of continuously drawing the fluid into the pump and sequentially passing the fluid through the introduction region and the discharge region. These regions are continuously formed in the space between the rotor surface and the chamber wall across the fluid inlet and fluid outlet. This type of configuration is referred to as a positive displacement pump, and each cycle of rotation discharges a substantially constant volume of fluid independent of inlet and outlet pressures, apart from the slight effect of fluid compression under pressure. . This type of pump is used to pump fluids with a wide range of viscosity from gases to relatively viscous liquids such as heavy oil and grease. Such pumps are relatively simple in construction and are preferred for a wide range of applications including industry, commercial, maritime, medical, and other fields of use. Furthermore, with appropriate modifications, such pumps can be diverted to turbines that convert the differential pressure between fluids into mechanical energy.

It is known that a rotary vane pump that uses an internal rotor or impeller that drives fluid can be used as both a pump and a turbine. For example, a previous U.S. patent by the inventor of the present application (see U.S. Pat. No. 6,053,065) describes a rotating device having a plurality of vanes, the stator of which includes a fluid inlet having a generally cylindrical bore. And having a fluid outlet. The rotor is mounted eccentrically on the bore (the rotor axis is displaced from the center axis of the bore), and a plurality of vanes project radially outward from the rotor, creating a sealing contact between the bore inner surface and the rotor I am doing so. This device is used as a turbine that converts flowing fluid energy into mechanical energy. Other arrangements are also known in which the rotor is eccentrically attached to the bore and a plurality of vanes protruding from the outer surface of the rotor are reciprocated relative to the rotor. The rotation of the rotor draws fluid into the space between the rotor and the inner wall of the bore, where the vanes are used to propel the fluid from the housing to the discharge conduit. The combination of the vane and the eccentric mounting of the rotor creates a unidirectional fluid flow and effectively separates the chamber into a plurality of inlet and outlet chambers.
US Pat. No. 6,554,596

  An object of the present invention is to obtain an improved rotary vane pump which can be used for a wide range of viscous fluids and is relatively simple and inexpensive.

  The first invention of the present invention is characterized by a rotary vane pump comprising the following elements.

A stator comprising a static pump housing in fluid communication with each other an internal pump chamber or bore having a fluid inlet, a fluid outlet, and a cylindrical region;

A cam-like rotor rotatably mounted in the cylindrical region of the pump chamber, having a central rotational axis and a cam outer surface in contact with the fluid to be pumped. The shape of the rotor is a first portion which is substantially opposite to each other and each has an equal radius, the opposite portions each having a reduced diameter and a first opposing portion which is in sealing contact with the vane on the inner surface of the housing bore. A substantially opposite second portion, and a space is formed between the rotor surface and the inner surface of the rotor bore for accommodating a certain amount of fluid that passes through the pump during rotor rotation. Such a space effectively forms an introduction region and a discharge region during rotor rotation.

-Any convenient means for rotationally driving the rotor, without limiting the type of motor, regardless of whether it is mechanically connected directly to the rotor or not. This drive means can be a fluid flow through the pump when the pump is used as a turbine.

-At least one vane attached to the housing and plunging into the pump chamber. A single vane is preferably provided, but a plurality of vanes may be provided. The vane is mounted to reciprocate relative to the housing and has a contact surface that contacts the cam surface of the rotor, and the pump chamber on both sides of the vane during the rotor rotation phase where the cam surface does not contact the chamber wall at the vane position. Is effectively divided into two regions. Each region on both sides of the vane is defined by the space between the rotor surface and the chamber wall. The first region effectively defines an introduction chamber, and the second region forms an exhaust chamber that maintains fluid separation between the inlet and outlet. Contact between the vane and the cam surface of the rotor results in rotor rotation that causes the vane to reciprocate.

  The rotor can have various cross-sectional shapes, for example, an elliptical shape or a substantially elliptical shape. As an alternative, the rotor is shaped with arms that are diametrically opposed to each other, each arm having a curved leading cam surface that raises the vane as the rotor rotates, and a flat or nearly flat tail edge surface. It is also possible to provide a stop member with which the vane whose reciprocating motion collides with the tail edge surface to prevent reverse rotation of the rotor. This configuration further increases the effective chamber volume. That is, only the leading surface, which is one side surface of each rotor arm, needs to be bowed outwardly. Other rotor configurations are within the scope of the present invention.

  The central axis of the vane (ie, the central plane that defines the center of the vane) is aligned with the rotational axis of the rotor or, for example, when applied to a rotor configuration of the type described above having a flat tail edge surface , It is arranged so as to be shifted from the rotation axis of the rotor. Preferably, there is provided a pressing displacement means for pressing the vane against the cam surface, such as (but not limited to) a spring or other member having a similar function. It is also possible to drive the vane using the pressure difference between the inlet and outlet of the pump. In this case, a conduit is provided from the pump outlet (where high fluid pressure is present) to the vane housing part that drives the vane in the direction of the rotor by expansion of the fluid. The vane is contained in a slot or track without this housing. The vane contact surface is provided with an elongated roller bearing or other low friction surface that reduces friction between the vane and the cam surface of the rotor. The vane is a flat panel-like member, and an enlarged portion is optionally provided on the lower edge that contacts the rotor. For example, a bulbous portion that protrudes outward from one side surface or both side surfaces of the vane is provided.

  Furthermore, the present invention can be made of any material or combination of such materials, such as various metals and plastics that meet the requirements of the pump environment. Further, the pump can be provided alone or as a component of another device.

  These and other features of the present invention will be described in detail hereinafter with reference to embodiments of the invention, but these descriptions do not limit the scope of the claims of the invention.

  In the present specification, including the claims, descriptions relating to various directions, for example, upward, downward, vertical, horizontal, etc., are described. These descriptions are merely for convenience and do not limit the scope of the invention in any way. One skilled in the art will readily appreciate that the present invention can be oriented in any state. Furthermore, the separation distance is determined based on strictly vertical, horizontal, and similar directions.

  Next, preferred embodiments of the present invention will be described with reference to the drawings. While the invention will be described with reference to the illustrated embodiments, it will be understood that the invention is not limited to such embodiments. On the contrary, it is intended to cover all modifications, changes, and equivalents within the scope of the invention as defined in the claims.

  An embodiment of a positive displacement vane pump 10 according to the present invention generally includes a static pump housing 12, which may be referred to herein as a “housing”. It has an internal chamber or bore 14 for receiving a reciprocating vane (sometimes abbreviated simply as “vane” herein) 22. 1-4, the pump housing 12 has an inlet 30 and an outlet 32 for fluid. It should be understood that the relative dimensions of these and other components of the pump are exemplary only and may vary within wide limits based on the specific pump requirements. Such modifications and changes can be easily made by those skilled in the art. The housing 12 has a bore 14 for receiving the rotor 20, which has a cylindrical lower portion 34, and an inner surface 36 of the lower portion 34 forms a smooth contact surface with which the rotor 20 contacts. . The rotor bore 14 has opposing side walls 38 that fit into end walls 39 of the rotor 20, as will be described later. (These portions 38, 39 are visible in FIGS. 6 and 7.) The inlet 30, rotor bore 14 and outlet 32 are in sequential fluid communication with one another. That is, at any point in the pump cycle, fluid communication between the inlet 30 and outlet 32 is caused by the combination of the rotor 20 and vane 22 and the inner surface 36 of the bore 14 in contact with each other, as will be described in detail below. Be blocked. In this way, the inlet and the outlet are in fluid communication with each other in that the fluid flowing into the inlet sequentially passes through the inlet, the rotor bore and the outlet.

  The housing 12 has a block 40 that houses and supports the reciprocating vane 22. The block has a vertical channel 42 that houses the vane, with the flat side of the channel contacting the other surface of the vane 22. The exterior of the vane block 40 protrudes upward from the pump so that sufficient space is created in the block to accommodate the vane 22 when the vane 22 is retracted. A threaded opening 44 is passed through the upper surface of the block, and the outside of the pump communicates with the inside of the channel 42. The spring tension adjusting screw 46 is inserted into the screw opening and is inserted into the upper end of the channel. A spring 48 is received in the channel 42 and presses the vane 22 against the lower rotor 20 as will be described in more detail below. A person skilled in the art can use any convenient pressure displacement means instead of the spring 48, such as a gas spring, an elastic member (elastomer rod), etc., which are also within the scope of the claims of the present invention. It will be clear.

  The rotor 20 has a central shaft 50, and the central shaft 50 is rotatably supported on a shaft mount 52 of a general design (not shown). The central shaft 50 is drivingly connected to a drive that rotates the rotor 20. Although this driver is not shown, it will be apparent to those skilled in the art that any driver means can be used to rotate the shaft and thus the rotor. For example, any type of motor, hydraulic drive or manually operated hand crank can be used based on the pump application. Similarly, as will be described below, the present invention can also be operated as a turbine, in which case the rotor 20 is driven to rotate by a differential pressure present between the inlet and outlet, passing through the pump. Fluid acts as drive means, and no drive means is required for the rotor. The rotor 20 is elongated and exists between the side walls 38 of the rotor bore. The end walls 39 on either side of the rotor 20 meet and contact corresponding side walls 38 of the bore 14 to prevent or minimize fluid leakage. Although a flat end wall 39 is preferred, the end wall 39 and the corresponding side wall 38 of the bore can be of any convenient shape or form. The rotor 20 is characterized by a non-circular shape having two equal first radii (a) facing each other in the diametrical direction defining a maximum rotor diameter at a predetermined point along the length direction. (For example, the rotor may be tapered along its length or other shapes.) This radius (a) defines the outer edges of the opposing arms 56 of the rotor, and thus the bore of the rotor. A rotor edge 54 is defined that contacts the 14 cylindrical inner surfaces. The rotor is further defined by a substantially diametrically opposed second radius (b) that defines a rotor minimum diameter. The rotor 20 and bore 14 may be tapered or otherwise shaped with radii (a) and (b) that vary along the length of the rotor.

  In the embodiment of FIGS. 1 to 4, the rotor 20 is constituted by two identically shaped paddles or arms 56 extending in opposite directions from the central axis. Each arm 56 has a curved leading surface 60 and a flat tail edge surface 62 opposite the leading surface. The tail edge surface 62 of the first paddle 56 meets the leading surface 60 of the opposite paddle 56. The stepped portion 64 has a feature that it joins between the tail edge surface 62 of the first paddle and the leading surface 60 of the second paddle on the opposite side, and becomes a step that goes downward from the leading surface to the tail edge surface. . The stepped portion 64 has a rounded edge that joins at an angled shoulder 66.

  The reciprocating vane 22 according to the first embodiment of the present invention is shown in more detail in FIGS. The vane 22 has a substantially flat plate shape having a flat front surface and a rear surface (however, other shapes having an arcuate shape when viewed in cross section) can be used. The vanes 22 have side shoulders 70 that oppose each other, such that the side shoulders 70 sandwich a central (optional) recessed panel 72 in a sandwich. The side shoulder 70 is integral with the panel 72 and the surface of the panel 72 is flush with the surface (this embodiment will be described in more detail with respect to the second embodiment in particular), FIG. As shown in FIG. 4, the panel 72 is recessed with respect to the side wall. The vane 22 and the channel 42 in the vane block 40 are shaped to fit closely together, exhibiting substantially imperviousness to fluid leakage and allowing the vane to reciprocate within the channel. The side shoulders 70 of the vanes 22 fit into corresponding recesses 74 in the housing 12 guide that align with the channels 42 on the side of the vane block. Preferably, the top surface 78 of the vane 22 is substantially flat and the side shoulder 70 projects downward beyond the lower edge of the center panel 72 as shown upside down in FIG. The lower end edge of the center panel 72 has a round protrusion 80 protruding in a bulbous side, and the round protrusion 80 defines the lower end edge of the center panel 72. The bulbous protrusion 80 increases the strength of the vane at the point where it contacts the rotor. In order to maintain sealing contact with the rotor, an elongated roller bearing 82 is provided at the lower edge of the center panel. The roller bearings 82 are fitted into corresponding receiving channels 84 extending laterally in the vane 22 across the lower edge. The roller bearing 82 is made of any convenient material, for example, stainless steel or Teflon (registered trademark).

  As another feature of the first embodiment, the vane 22 is positioned in the housing 12 so as to be offset from the rotational axis of the rotor 20, and when viewed in a side view, the central axis of the vane is on the left side (downstream side) of the rotor axis. ) That is, it is offset toward the downstream side of the rotor axis. As described below, the shape of the rotor 20 relative to the offset position of the vanes 22 allows for one-way operation of the rotor, preventing the rotor from spinning in the reverse direction and counterflow from the outlet to the inlet. According to this shape, the chamber volume can be optimized and the flow rate can be increased. The amount of offset of the vane 22 relative to the rotor axis is a function of the rotor thickness, i.e., the horizontal distance between the flat rear surface of the rotor and the vertical radius of the rotor 20 when the rotor 20 is in a vertical state. The vanes 22 are displaced from the rotor axis by an equal horizontal distance (c). With this amount of displacement, the vane 22 can slide down to a position where it completely contacts the flat side surface of the rotor when the rotor is in the vertical state shown in FIGS. 2 (f) and 2 (g).

  The operation of the first embodiment will be described with reference to FIGS. 2 (a) to 2 (h). In the first position shown in FIG. 2A, the rotor 20 is in a substantially horizontal state, and the vane 22 takes a position protruding downward so as to contact the rotor 20. As shown in FIG. 2B, when the rotor rotates in the clockwise direction, the effective dimension of the introduction portion of the rotor chamber 14 is expanded and fluid is drawn into the chamber 14. As the rotor continues to rotate as shown in FIGS. 2 (c) to 2 (e), the relative dimension of the chamber introduction portion continues to expand, and the vane 22 comes into contact with the leading surface 60 of the rotor 20 and is pushed upward. The rotor reaches a position in which it is in a substantially vertical state as shown in FIG. At this point, the flat tail edge surface 62 of the rotor is aligned with the corresponding surface of the vane 22 and the vane 22 moves downward due to the pressing force of the internal spring 48. Preferably, this spring tension is adjusted so that the vane moves downward rapidly. The vane protrudes as much as possible in the state shown in FIG. 2G, and further downward movement of the vane comes into contact with the stepped portion 64 of the rotor 20 protruding radially outward from the flat tail edge surface 62. Be blocked. When the vane 22 abuts the tail edge surface 62, the rotor 20 is prevented from rotating in the reverse direction (counterclockwise).

  The tail surface 62 need not be flat if it is not necessary to prevent counter-rotation, but is merely to achieve the purpose of increasing the effective volume of the rotor bore 14. . Thus, this feature is obtained if the tail edge surface 62 is a surface that is slightly flatter than the leading surface 60.

  As shown in FIG. 2 (h), as the rotor continues to rotate, the vane 22 is raised, pushing fluid out of the outlet 32 and forming the other inlet portion of the chamber at the fluid inlet.

  A second embodiment of the present invention is shown in FIGS. In the second embodiment, the inlet 30 and the outlet 32 are parallel to each other and protrude from the upper surface of the pump 10. However, the horizontal inlet and the outlet are slightly changed as in the first embodiment. In addition, at least one of the inlet and the outlet can be arranged at an arbitrary position. The rotor 20 of the second embodiment has a substantially elliptical cross-sectional shape that is symmetrical and can rotate in either direction so that the inlet and outlet conduits are reversed and function based on the direction of rotor rotation. To. The vane 22 (shown in more detail in FIGS. 8 and 9) is substantially similar to the vane of the first embodiment, but with the bulbous portion 80 in the lower edge region of the vane evenly laterally toward both sides of the vane. Make it protrude. The vane 22 is a single panel structure (without protruding side rails), and on both sides, protrudes below the lower edge of the vane, as shown in more detail in FIGS. A droop stop is provided.

  As another feature of the second embodiment, as shown in FIGS. 10 and 11, the pressure displacement means is not accommodated in the vane block 40, but is retracted into the corresponding opening 92 in the vane. A spring-loaded pressure rod 90 is provided. 8 and 9 show a state in which the push rod is retracted, and FIGS. 10 and 11 show a state in which the push rod protrudes. These push rods 90 can be displaced in a direction protruding from the vane by any convenient press displacement means, for example, a spring 94 or other elastic member.

  The vane block 40 has a drain opening or slot 96 communicating with the vane receiving channel 42 so that fluid leaking from the main channel 42 can be discharged to the main fluid outlet 32. Slot 96 potentially also serves a second function. When the slot 96 has a directivity such that it opens toward the high pressure side of the pump (ie, the downstream outlet), the slot 96 drives the vane 22 using the inlet / outlet differential pressure. Or assisting vane drive. A relatively high pressure fluid stream flows into the channel 42 in the space above the vane. Since this fluid has a relatively high pressure, a bias force is applied to the vane 22 and is pressed downward so as to be pressed against the rotor 20. This effect is enhanced by providing a partially enclosed inlet chamber 95 and outlet chamber 97, respectively, and opening the slot 96 into the outlet chamber 97.

  In particular, as shown in FIG. 7, the vane block 40 simply accommodates only the upper portion of the vane 22, and the lower portion of the vane 22 protrudes downward into the main chamber 14.

  Opposite track slots aligned with the vane channel are provided on the side wall of the chamber so as to accommodate and guide the end wall portion of the vane.

  In particular, as shown in FIG. 5, the vane 22 is aligned with the rotation axis of the rotor 20.

  In operation, the second embodiment operates in the same manner as the first embodiment, but a symmetrical elliptical rotor does not have a reverse rotation prevention function. The second embodiment can be used in particular for reversible rotary pumps, i.e. pumps that can discharge fluid into one of the conduits by reversing the direction of rotation of the rotor 20.

  A third embodiment of the present invention is shown in FIGS. This embodiment is similar to the second embodiment having a generally elliptical rotor 20. However, the vane 22 is offset from the rotation axis of the rotor 20 toward the outlet side (downstream side) of the vane 22. Due to the offset position of the vanes, the rotor 20 is pushed upward toward the retracted position more efficiently when the rotor 20 rotates. Another difference from the second embodiment is the shape of the vane bulb-shaped downward protrusion 80, and the third embodiment is similar to the shape of the protrusion in the first embodiment. Further, in this third embodiment, the areas of the inlet 30 and the outlet 32 are different from each other, that is, the inlet and the outlet are offset from each other and arranged in a substantially horizontal direction, and the inlet is raised with respect to the outlet. Communicates with the chamber in position.

  Although the invention has been described with reference to particular embodiments, those skilled in the art will recognize that the invention may be omitted, including omitting non-essential elements and adding other elements within the scope of the claims. It will be understood that changes and modifications to the elements described in the document are within the scope of the invention. The scope of the present invention is defined in the claims that may be amended from time to time, and includes functionally or mechanically equivalent components, elements, or methods of operation.

1 is a diagrammatic cross-sectional view of a first embodiment of the present invention. It is a diagrammatic sectional view showing the sequential position of the rotor and the reciprocating vane in the pump cycle of the first embodiment. It is a perspective view of the vane part of 1st Example. It is the diagrammatic partial side view which showed the hidden part of the vane of the 1st example with the broken line. FIG. 6 is a diagrammatic cross-sectional view of a second embodiment of the present invention. It is a diagrammatic perspective view showing a part of the second embodiment. FIG. 6 is another diagrammatic perspective view showing a part of the second embodiment. It is another side view of the vane part of 2nd Example. It is another perspective view of the vane part of 2nd Example. It is further another perspective view of the vane part of 2nd Example. It is another different perspective view of the vane part of 2nd Example. It is a diagrammatic perspective view of the third embodiment of the present invention. It is the perspective view seen from the exterior of 3rd Example.

Explanation of symbols

10 Vane pump 12 Pump housing 14 Bore 20 Rotor 22 Reciprocating vane 30 Inlet 32 Outlet 34 Lower part 36 Inner surface 38 Side wall 39 End wall 40 Block 42 Vertical channel 44 Threaded opening 46 Spring tension adjusting screw 48 Spring 50 Center shaft 54 Rotor edge 56 Arm 60 Leading surface 62 Tail edge surface 64 Stepped portion 66 Shoulder portion 70 Side shoulder portion 72 Panel 74 Depression 78 Top surface 80 Projection portion 82 Roller bearing 84 Housing channel 90 Spring load pressing rod 92 Opening 94 Spring 95 Inlet chamber 96 Drain opening Or slot 97 outlet chamber

Claims (46)

In rotary vane pumps,
A static housing having a fluid inlet, a fluid outlet, and a pump chamber having at least a portion of a circular cross-section bore in fluid communication with each other;
A rotor rotatably mounted within a circular cross-section portion of the bore, the rotor having a central axis of rotation and a cam surface having a non-circular cross-section;
At least one vane mounted in the housing to reciprocate between a projecting position and a retracted position relative to the housing, the contact surface being in sealing contact with the cam surface of the rotor; A vane pump having a vane reciprocated by rotation of the rotor, and configured to maintain fluid separation between the inlet and the outlet by the vane and the rotor.   The vane pump according to claim 1, further comprising a driving means for rotating the rotor.   2. The vane pump according to claim 1, further comprising pressing displacement means that acts between the vane and the housing to press the vane against the rotor.   The vane pump according to claim 1, wherein the vane is slidably received in a channel formed in the housing so as to open to a chamber of the pump.   The vane pump according to claim 1, comprising a single vane.   The vane pump according to claim 1, wherein the vane is disposed by being displaced from a rotation axis of the rotor in a downstream direction of the pump.   The vane pump according to claim 6, wherein the rotor has a substantially oval cross section.   The vane pump according to claim 1, wherein the rotor is configured to have portions having substantially equal radii of maximum length so as to be in sliding contact with the inner surface of the bore and substantially opposed to each other.   The portion of the rotor has a curved leading surface that forms a cam surface that raises the vane as the rotor rotates, and a substantially flat tail edge surface, the vane correspondingly contacting the tail edge surface Having a flat-shaped surface, the vane being arranged offset with respect to the rotation axis of the rotor, and the tail edge surface of the rotor being completely aligned with the corresponding flat surface of the vane when the vane is in a protruding position The vane pump according to claim 8, wherein the vane pump is in contact with the rotor to prevent reverse rotation of the rotor.   The vane pump according to claim 8, wherein the rotor portion has a curved leading surface forming a cam surface and a tail edge surface that is a flatter surface than the leading surface.   The vane pump according to claim 1, wherein the vane has a low friction contact member that maintains sealing contact with the rotor.   The vane pump according to claim 11, wherein the low friction contact member is constituted by a roller bearing that fits into a partially recessed channel formed in the vane.   The vane pump according to claim 11, wherein the vane is configured to have a thick region that protrudes laterally from the contact surface in a vane region adjacent to the contact member.   The vane pump according to claim 11, wherein a drain communicating with the channel is provided so as to discharge fluid from the channel.   The vane pump according to claim 14, wherein the drain is opened at an outlet of a fluid having a relatively high fluid pressure, and the vane is pressed toward the rotor by the relatively high fluid pressure on the outlet side.   2. The vane pump according to claim 1, wherein the housing has a side wall on a side, and a groove hole for receiving and guiding the vane is provided on at least one side wall. In rotary vane pumps,
A static housing having a fluid inlet, a fluid outlet, and a pump chamber having at least a portion of a circular cross-section bore in fluid communication with each other;
A rotor rotatably mounted within a circular cross section of the bore, the rotor having a central axis of rotation and a cam surface having a non-circular cross section;
At least one vane mounted in the housing to reciprocate between a projecting position and a retracted position relative to the housing, the contact surface being in sealing contact with the cam surface of the rotor; A vane reciprocated by rotation of the rotor, and configured to maintain fluid separation by the vane and the rotor between the inlet and the outlet;
2. The vane pump according to claim 1, wherein the rotor is configured to have portions having opposite radii having the same maximum length so as to come into sliding contact with the inner surface of the bore.   The vane pump according to claim 17, further comprising driving means for rotating the rotor.   The vane pump according to claim 17, further comprising pressing displacement means that acts between the vane and the housing to press the vane against the rotor.   The vane pump according to claim 17, wherein the vane is slidably received in a channel formed in the housing so as to open to a chamber of the pump.   The vane pump according to claim 17, comprising a single vane.   18. The vane pump according to claim 17, wherein the vane is configured by a substantially panel-shaped member having a central axis, and the central axis is displaced from a rotation axis of the rotor toward a downstream side of the pump.   The vane pump according to claim 22, wherein a cross section of the rotor is substantially elliptical.   18. The vane pump according to claim 17, wherein the rotor is configured so as to have portions having substantially equal radii of maximum length so as to be in sliding contact with the inner surface of the bore and substantially opposed to each other.   The portion of the rotor has a curved leading surface that forms a cam surface that raises the vane as the rotor rotates, and a substantially flat tail edge surface, the vane correspondingly contacting the tail edge surface Having a flat-shaped surface, the vane being arranged offset with respect to the rotation axis of the rotor, and the tail edge surface of the rotor being completely aligned with the corresponding flat surface of the vane when the vane is in a protruding position 25. A vane pump according to claim 24, wherein the vane pump prevents contact and reverse rotation of the rotor.   25. The vane pump according to claim 24, wherein the portion of the rotor is configured to have a curved leading surface forming a cam surface and a tail edge surface that is a flatter surface than the leading surface.   The vane pump according to claim 17, wherein the vane includes a low friction contact member that maintains sealing contact with the rotor.   28. A vane pump according to claim 27, wherein the low friction contact member comprises a roller bearing that fits into a partially recessed channel formed in the vane.   28. The vane pump according to claim 27, wherein the vane is configured to have at least one bulb-shaped projecting portion projecting laterally in a region of the vane adjacent to the contact member.   The vane pump according to claim 17, further comprising a drain communicating with the channel so as to discharge fluid from the channel.   The vane pump according to claim 30, wherein the drain is opened at an outlet of a fluid having a relatively high fluid pressure, and the vane is pressed toward the rotor by the relatively high fluid pressure on the outlet side.   The vane pump according to claim 17, wherein the housing has a side wall on a side, and a groove hole for receiving and guiding the vane is provided on at least one side wall. In rotary vane pumps,
A static housing having a fluid inlet, a fluid outlet, and a pump chamber having at least a portion of a circular cross-section bore in fluid communication with each other;
A rotor rotatably mounted within a circular cross-section portion of the bore, the rotor having a central axis of rotation and a cam surface having a non-circular cross-section;
At least one vane mounted in the housing to reciprocate between a projecting position and a retracted position relative to the housing, the contact surface being in sealing contact with the cam surface of the rotor; A vane reciprocated by rotation of the rotor, and configured to maintain fluid separation between the inlet and the outlet by the vane and the rotor;
The rotor is configured to have portions having opposite radii having the same maximum length so as to come into sealing sliding contact with the inner surface of the bore. A curved leading surface forming a cam surface that raises the surface and a substantially flat tail edge surface, the vane having a corresponding flat surface in contact with the tail edge surface, and the vane to the rotor So that the tail edge surface of the rotor is in full contact with the corresponding flat surface of the vane to prevent reverse rotation of the rotor when the vane assumes a protruding position. Vane pump characterized by that.   34. The vane pump according to claim 33, further comprising driving means for rotating the rotor.   34. The vane pump according to claim 33, further comprising pressing displacement means that acts between the vane and the housing to press the vane against the rotor.   The vane pump according to claim 33, wherein the vane is slidably received in a channel formed in the housing so as to open to a chamber of the pump.   34. A vane pump according to claim 33 having a single vane.   34. The vane pump according to claim 33, wherein the vane is constituted by a substantially panel-shaped member having a central axis, and the central axis is aligned with a rotation axis of the rotor.   39. A vane pump according to claim 38, wherein the rotor has a substantially oval cross section.   34. The vane pump according to claim 33, wherein the rotor is configured to have portions having substantially equal radii of maximum length so as to be in sliding contact with the inner surface of the bore and substantially opposed to each other.   34. The vane pump according to claim 33, wherein the vane includes a low friction contact member that maintains sealing contact with the rotor.   42. A vane pump according to claim 41, wherein the low friction contact member comprises a roller bearing that fits into a partially recessed channel formed in the vane.   42. The vane pump according to claim 41, wherein the vane is configured to have at least one bulb-shaped projecting portion projecting laterally in a region of the vane adjacent to the contact member.   34. The vane pump according to claim 33, wherein a drain communicating with the channel is provided so as to discharge fluid from the channel.   45. The vane pump according to claim 44, wherein the drain is opened at an outlet of a fluid having a relatively high fluid pressure, and the vane is pressed toward the rotor by the relatively high fluid pressure on the outlet side.   34. The vane pump according to claim 33, wherein the housing has a side wall on a side, and a groove hole for receiving and guiding the vane is provided on at least one side wall.

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